US7384198B2 - Rolling bearing - Google Patents

Rolling bearing Download PDF

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Publication number
US7384198B2
US7384198B2 US09/925,020 US92502001A US7384198B2 US 7384198 B2 US7384198 B2 US 7384198B2 US 92502001 A US92502001 A US 92502001A US 7384198 B2 US7384198 B2 US 7384198B2
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United States
Prior art keywords
rolling bearing
rolling
bearing
rotary body
grease
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related, expires
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US09/925,020
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English (en)
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US20020051595A1 (en
Inventor
Fusasuke Gotoh
Hiroshi Ishiguro
Naoki Fukuda
Toshihisa Ohata
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NSK Ltd
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NSK Ltd
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Assigned to NSK LTD. reassignment NSK LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FUKUDA, NAOKI, GOTOH, FUSASUKE, ISHIGURO, HIROSHI, OHATA, TOSHIHISA
Publication of US20020051595A1 publication Critical patent/US20020051595A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D27/00—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor
    • F16D27/10—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings
    • F16D27/108—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members
    • F16D27/112—Magnetically- or electrically- actuated clutches; Control or electric circuits therefor with an electromagnet not rotating with a clutching member, i.e. without collecting rings with axially movable clutching members with flat friction surfaces, e.g. discs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/66—Special parts or details in view of lubrication
    • F16C33/6603—Special parts or details in view of lubrication with grease as lubricant
    • F16C33/6633—Grease properties or compositions, e.g. rheological properties
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
    • F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
    • F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
    • F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
    • F16C2240/70—Diameters; Radii
    • F16C2240/76—Osculation, i.e. relation between radii of balls and raceway groove
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2361/00—Apparatus or articles in engineering in general
    • F16C2361/63—Gears with belts and pulleys

Definitions

  • the present invention relates to a rolling bearing structured such that a rotary body with an outer ring fitted therewith and a shaft with an inner ring fitted therewith can be connected together by a clutch mechanism and, when the rotary body and shaft are connected together by the clutch mechanism, with no relative rotation between the inner and outer rings, the rolling bearing can be used on receiving a rotation load; and, in more particular, to an improvement in such rolling bearing which can prevent occurrence of fretting in the bearing raceway surfaces thereof to thereby enhance the life thereof.
  • FIGS. 1 and 2 show the states of use of a rolling bearing.
  • a rolling bearing 1 shown in FIGS. 1 and 2 is a combined bearing, in which, between the raceway surface 2 a of an outer ring 2 and the raceway surface 3 a of an inner ring 3 , there is interposed spherical-shaped rolling elements 4 .
  • the rolling elements 4 are respectively held by a retainer (not shown) in such a manner that they are spaced at given intervals in the peripheral direction of the raceway surfaces 2 a , 3 a. Also, grease is sealed in by a seal (not shown).
  • the outer ring 2 is fitted with the inner periphery of a rotary body 6
  • the inner ring 3 is fitted with the outer periphery of a shaft 8 .
  • the rotary body 6 is a pulley which can be driven through a belt wound on a belt groove 6 a formed in the outer periphery thereof, while the other end portion (not shown) of the rotary body 6 provides an output end thereof.
  • the rotary body 6 and shaft 8 can be connected together by a clutch mechanism 12 .
  • the clutch mechanism 12 is an electromagnetic clutch which is composed of a clutch plate 13 fixed to the end portion of the shaft 8 and an electromagnetic drive portion 14 for attracting the outer peripheral portion of the clutch plate 13 to the rotary body 6 using an electromagnetic force.
  • FIG. 1 shows a clutch-off state in which the rotary body 6 and shaft 8 can be rotated with respect to each other, whereas FIG. 2 shows a clutch-on state in which the rotary body 6 a nd shaft 8 is prevented against their relative rotation.
  • an initial radial clearance between inner and outer rings is set in such a manner that a bearing effective clearance when the rolling bearing is incorporated into between the rotary body 6 and shaft 8 can be reduced as much as possible.
  • the invention aims at eliminating the above-mentioned problems found in the conventional rolling bearings. Accordingly, it is an object of the invention is to provide a rolling bearing which, with no relative rotation between inner and outer rings, can be used on receiving a rotation load, wherein there is eliminated a fear of incurring the complication of a process for manufacturing the component parts of the rolling bearing, fretting can be prevented inexpensively and positively, generation of strange sounds and reduction in the life of the bearing due to local wear caused by such fretting can be prevented, and reduction in the life of grease due to worn powder produced in the local wear can be prevented.
  • a rolling bearing structured such that a plurality of rolling elements are held between inner and outer rings by a retainer, grease is sealed in by a seal, a rotary body with the outer ring fitted therewith and a shaft with the inner ring fitted therewith can be connected together by a clutch mechanism, and, when the rotary body and shaft are connected together by the clutch mechanism, with no relative rotation between the inner and outer rings, the rolling bearing can be used on receiving a rotation load, wherein an initial radial clearance between the inner and outer rings is set in such a manner that a bearing effective clearance when the bearing is incorporated between the rotary body and shaft provides a positive value.
  • the initial radial clearance may be set as large as possible unless a defect such as a ball run-out/onto-groove-shoulder phenomenon can occur.
  • the initial radial clearance may be set such that the bearing effective clearance is in the range of 0.020-0.060 mm, preferably, in the range of 0.040-0.60 mm.
  • the rotary body and shaft are connected together by the clutch mechanism in such a manner that they can be rotated integrally, so that there is no relative rotation between the inner and outer rings of the rolling bearing.
  • the fretting in the case of the structure according to the invention, in a rolling bearing which can be used on receiving the rotation load with the relative rotation between the inner and outer rings zero, there is no fear of incurring the complication of the process for manufacturing the component parts of the rolling bearing, the fretting can be prevented inexpensively and positively, generation of strange sounds and the reduction in the life of the bearing due to the local wear caused by the fretting can be prevented, and the reduction in the life of grease due to the worn powder produced in the local wear can also be prevented.
  • the depths of the respective grooves formed in the inner and outer rings may be set 17% or more of the diameter of the rolling element
  • the interference of the seal lip of the seal may be set 60% or more of the axial clearance
  • the fretting resistance can be improved.
  • FIG. 1 is a longitudinal section view of an embodiment of a rolling bearing according to the invention and, in particular, a longitudinal section view thereof when the inner and outer rings of the rolling bearings can be rotated with respect to each other because a clutch mechanism is off;
  • FIG. 2 is a longitudinal section view of the embodiment of a rolling bearing according to the invention and, in particular, a longitudinal section view thereof when the inner and outer rings of the rolling bearings are prevented against rotation with respect to each other because the clutch mechanism is on;
  • FIGS. 3( a )-( e ) are respectively explanatory views of variations in a load direction when the inner and outer rings are driven or rotated integrally in the on state of the clutch mechanism shown in FIG. 2 ;
  • FIG. 4 is a view of the correlation between the number of rotations of the inner and outer rings and the behavior of a retainer (rolling element) when a bearing effective clearance is varied in the on state of the clutch mechanism shown in FIG. 2 ;
  • FIGS. 5( a ) and ( b ) are respectively section views of reduction in the bearing effective clearance corresponding to the inclinations of the inner and outer rings;
  • FIG. 6 is an explanatory view of the action of a centrifugal force applied to the respective rolling elements when the inner and outer rings are rotated integrally at a high speed;
  • FIGS. 7( a )-( e ) are respectively explanatory views of variations in a load direction when the inner and outer rings are driven or rotated integrally;
  • FIG. 8( a ) is a section view to show a contact state between a rolling element and the raceway surface of an inner ring when they are just below the load direction and on the opposite position; and, FIG. 8( b ) is an explanatory view of contact areas S 1 , S 2 between the rolling element and the raceway surface of the inner ring when they are just below the load direction and on the opposite position;
  • FIG. 9 is a section view to explain the interference of the seal lip
  • FIG. 10 is a graphical representation of the results obtained when Andelon values of the bearing are measured using several kinds of grease differing in the base oil dynamic viscosity.
  • FIGS. 1 to 6 show an embodiment of a rolling bearing according to the invention.
  • FIG. 1 is a longitudinal section view of an embodiment of a rolling bearing according to the invention, in particular, a longitudinal section view thereof when the inner and outer rings of the rolling bearings can be rotated with respect to each other because a clutch mechanism is off
  • FIG. 2 is a longitudinal section view of the embodiment of a rolling bearing according to the invention, in particular, a longitudinal section view thereof when the inner and outer rings of the rolling bearings are prevented against rotation with respect to each other because the clutch mechanism is on
  • FIG. 3 is an explanatory view of variations in a load direction when the inner and outer rings are driven or rotated integrally while the clutch mechanism shown in FIG. 2 is on;
  • FIG. 1 is a longitudinal section view of an embodiment of a rolling bearing according to the invention, in particular, a longitudinal section view thereof when the inner and outer rings of the rolling bearings can be rotated with respect to each other because a clutch mechanism is off
  • FIG. 2 is a longitudinal section view of the
  • FIG. 4 is a view of the correlation between the number of rotations of the inner and outer rings and the behavior of a retainer (rolling body) when a bearing effective clearance is varied while the clutch mechanism shown in FIG. 2 is on;
  • FIG. 5 is a section view of reduction in the bearing effective clearance corresponding to the inclinations of the inner and outer rings; and
  • FIG. 6 is an explanatory view of the action of a centrifugal force applied to the respective rolling elements when the inner and outer rings are rotated integrally at a high speed.
  • the rolling bearing 1 according to the present embodiment, schematically, has the same structure as shown in FIGS. 1 and 2 . That is, the rolling bearing 1 is a combined ball bearing in which, between the raceway surface 2 a of an outer ring 2 and the raceway surface 3 a of an inner ring 3 , there are interposed spherical-shaped rolling elements 4 .
  • the rolling elements 4 are held at given intervals in the peripheral directions of the respective raceway surfaces 2 a and 3 a by a retainer (not shown).
  • grease is sealed in by a seal.
  • the outer ring 2 is fitted with the inner periphery of a rotary body 6
  • the inner ring 3 is fitted with the outer periphery of a shaft 8 .
  • the rotary body 6 is a pulley which can be driven through a belt wound around a belt groove 6 a formed in the rotary body 6
  • the shaft 8 is structured such that the other end portion thereof (not shown) provides its output end.
  • the rotary body 6 and shaft 8 can be connected together by a clutch mechanism 12 .
  • the clutch mechanism 12 is an electromagnetic clutch which is composed of a clutch plate 13 fixed to the end portion of the shaft 8 and an electromagnetic drive portion 14 for attracting the outer peripheral portion of the clutch plate 13 to the rotary body 6 using an electromagnetic force.
  • FIG. 1 shows a clutch-off state in which the rotary body 6 and shaft 8 can be rotated with respect to each other
  • FIG. 2 shows a clutch-on state in which the rotary body 6 and shaft 8 is prevented against their relative rotation.
  • the rolling element 4 according to the rotation of the outer and inner rings 2 , does roll on the actual raceway surface 3 a of the inner ring 3 but rolls while shifting on a virtual inscribed circle C shown by broken lines in FIG. 3 ; that is, as shown by arrow marks (A)-(E) in FIGS.
  • the fretting can be prevented inexpensively and positively, generation of strange sounds and reduction in the life of the rolling a bearing due to local wear caused by the fretting can be prevented, and reduction in the life of the grease caused by worn powder due to the local wear can be prevented.
  • the present inventors in order to confirm the above-mentioned operation effects due to the bearing effective clearance, checked the presence or absence of the movement of the rolling body (retainer) on the raceway surface with respect to previously-set bearing effective clearances. The results of the our check are shown in FIG. 4 .
  • bearing effective clearances there were used four kinds of clearances, specifically, 0.01 mm, 0.023 mm, 0.042 mm, and 0.060 mm. And, for the respective bearing effective clearances, the presence or absence of the movement of the rolling element 4 was sampled and checked.
  • the diameter D 2 of the raceway surface 2 a of the outer ring 2 , the outside diameter d 4 of the rolling element 4 , and the diameter D 3 of the raceway surface 3 a of the inner ring 3 shown in FIG. 5( a ) are respectively changed into D 2 ⁇ , d 4 ⁇ , and D 3 ⁇ , so that the bearing effective clearance is narrowed down to ⁇ R s .
  • the above-mentioned contact position can be shifted more smoothly.
  • the respective groove depths of the raceway surface 3 a of the inner ring 3 and the raceway surface 2 a of the outer ring 2 may be designed such that they are 17% or more of the diameter of the rolling element 4 .
  • the bearing effective clearance is defined to be 0.020 mm or more, there is a fear that the play of the rolling bearing can increase to thereby lower the ball run-onto-groove-shoulder.
  • the respective groove depths of the raceway surfaces 3 a , 2 a of the inner and outer rings to be 17% or more of the diameter of the rolling element 4 , the lowering of the run-onto-top property can be restricted.
  • the bearing effective clearance is defined to be 0.020 mm or more, there also arises a fear that, in case where a contact seal is used, grease can leak.
  • the interference A of the seal lip 22 of the seal 20 may be set at 60% or more of the axial clearance so as to be able to prevent the leakage of the grease (not shown).
  • reference character 21 designates a base member which is made of metal and forms the seal 20
  • 10 stands for a retainer.
  • the sealed grease is not limited to a special one but, preferably, there may be used base oil having a dynamic viscosity of 80 mm 2 /s or more at 40° C.
  • base oil having a dynamic viscosity of 80 mm 2 /s or more at 40° C.
  • lithium soap was compounded in the same quantity into four kinds of synthetic oil (poly- ⁇ -olefin oil) differing in the dynamic viscosity at 40° C. to thereby prepare four kinds of grease; these four kinds of grease were respectively loaded into test bearings (type number: 6202, effective clearance: 0 mm (the clearance is eliminated by an axial load)) so that the grease occupies 35 volume percent of the bearing space; and, the grease was sealed in by seals. And, vibration tests were conducted on the respective test bearings in their stationary states and the Andelon values of the test bearings before and after the tests were measured. This Andelon value measurement means that the larger the Andelon values are, the more often strange sounds due to the fretting wear occur.
  • the ball run-onto-groove-shoulder property was evaluated. That is, there were prepared test bearings each having an inside diameter ⁇ 50 mm, an outside diameter ⁇ 72 mm, a width 12 mm, an effective clearance 0.006 mm, and respectively having different groove depths, grease prepared by compounding lithium soap into poly- ⁇ -olefin oil was loaded into the test bearings in such a manner that the grease occupies 35 volume percentage of the bearing space, and the grease was sealed in by seals. And, the test bearings were rotated under the axial load of 4900N and were checked for the presence or absence of the ball run-onto-groove-shoulder property. The results of this check are shown in FIG.
  • the ball run-onto-groove-shoulder allowance shows [ ⁇ ].
  • the above embodiment is an embodiment of a rolling bearing for use in, for example, a supercharger, in which, when an electromagnetic clutch is on, the rotary body 6 is rotated through the belt and the rotation of the rotary body 6 is transmitted to the shaft 8 ; and, when the electromagnetic clutch is off, the rotary body 6 is rotated through the belt but the shaft 8 remains stationary.
  • the rolling bearing may also be used in another embodiment, that is, the input and output sides of the rotation force may be reversed.
  • the invention may also apply to a structure such as a rolling bearing for use in a crankshaft, in which, when an electromagnetic clutch is on, the shaft 8 serves as a drive side and the rotary body 6 rotates with the relative rotation zero; and, when the electromagnetic clutch is off, the rotary body 6 rotates through the belt, whereas the shaft 8 remains stationary.
  • a structure such as a rolling bearing for use in a crankshaft, in which, when an electromagnetic clutch is on, the shaft 8 serves as a drive side and the rotary body 6 rotates with the relative rotation zero; and, when the electromagnetic clutch is off, the rotary body 6 rotates through the belt, whereas the shaft 8 remains stationary.
  • the fretting in a rolling bearing which, with the relative rotation between inner and outer rings zero, can be used on receiving a rotation load, there is eliminated a fear of incurring the complication of the process for manufacturing the component parts of the rolling bearing, the fretting can be prevented inexpensively and positively, generation of strange sounds and reduction in the life of the rolling bearing due to local wear caused by the fretting can be prevented, and reduction in the life of the grease caused by worn powder due to the local wear can be prevented.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)
US09/925,020 2000-08-09 2001-08-09 Rolling bearing Expired - Fee Related US7384198B2 (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2000241409 2000-08-09
JPP.2000-241409 2000-08-09
JPP.2001-242387 2001-08-09
JP2001242387A JP2002122151A (ja) 2000-08-09 2001-08-09 転がり軸受

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US20020051595A1 US20020051595A1 (en) 2002-05-02
US7384198B2 true US7384198B2 (en) 2008-06-10

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20170101995A1 (en) * 2014-04-01 2017-04-13 Kabushiki Kaisha Toyota Jidoshokki Electric supercharger and supercharging system
US10119568B2 (en) * 2016-10-21 2018-11-06 Jtekt Corporation Rolling bearing

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4015360B2 (ja) * 2000-12-21 2007-11-28 Ｎｔｎ株式会社 プーリ用玉軸受及びプーリ
JP2008185107A (ja) * 2007-01-29 2008-08-14 Nsk Ltd 玉軸受
DE102007061589B4 (de) 2007-01-29 2017-06-22 Nsk Ltd. Kugellager und Halterungskonstruktion
JP5305125B2 (ja) * 2007-12-18 2013-10-02 Ｎｔｎ株式会社 オルタネータ用転がり軸受
JP5392595B2 (ja) * 2008-04-08 2014-01-22 Ｎｔｎ株式会社 グリース封入外輪回転用転がり軸受
JP2010190242A (ja) * 2009-02-16 2010-09-02 Nsk Ltd 軸受ユニット
JP2017020581A (ja) * 2015-07-10 2017-01-26 日本精工株式会社 プルタイプクラッチレリーズ軸受装置用玉軸受

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